Dump valve fob hydraulic couplings



Feb. 24, 1948. N. L. ALISON Re. 22,975

DUMP VALVE FOR HYDRAULIC COUPLINGS Original Filed Sept. 24, 1940 4 Sheets-Sheet 1 5y a HTTOQ/VEY-S Feb. 24, 1948. N, ALISON Re. 22,975

DUMP VALVE FOR HYDRAULIC COUPLINGS Original Filed Sept. 24, 1940 4 Sheets-Sheet 2 :EIEEZ 42 4 3 1 W-arm? vv I I I INVENTOQ NOAH L. ALISON BY 3W #5W HTTOQNE 6 Feb. 24, 1948. N. 1 ALISON DUMP VALVE FOR HYDRAULIC COUPLINGS Original Filed Sept. 24, 1940 4 Sheets-Sheet I5 FIEra Y mm 5 r N N Q 5 0 vm W WW a Feb. 24, 1948. N, ALISON Re. 22,975

DUMP VALVE FOR HYDRAULIC COUPLINGS Original Filed Sept. 24, 1940 4 Sheets-Sheet 4 B3 INVENTO NOAH L. ALI N By SWTSW ATTORNEYS Reiseued Feb. 24, 1948 nmur VALVE roa mmmmc cournmcs Noah L. Alison, Phoenix, Aria, assignor to The American Blower Corporation, Detroit, Mich, a corporation of Delaware Original No. 2,325,090,1lated July 2'1, 1943, Serial No. 358,144, September 24. 1940. Application for reissue September 8, 1947. Serial No. 172,828.

1 11 Claims.

This invention relates to hydraulic couplings,

and in particular to means for controlling the actuation of dumping valves for emptying such couplings.

It is an object of the invention to provide a hydraulic coupling having a casing with dumping valves for emptying the casing of working liquid, in which the operation of the dumping valves is not affected by the centrifugal force imparted upon the driving fluid during the operation of the coupling, and is hydraulically counterbalanced against centrifugal force to prevent valve sticking.

It is another object of the invention to provide a hydraulic coupling having a dumping valve including a reciprocable member and a cylinder for controlling the discharge of working fluid from the coupling members, in which undesired dirt particles in the working fluid are prevented from accumulating between the reciprocable member and the cylinder walls engaged thereby by precollection of such foreign material before they can reach said valve.

It is an object of the invention to precollect dirt particles from the oil in the coupling prior to the oil entering into the dumping valve by centrifugal action of the coupling, and to discharge such dirt from the oil line leading to the valve.

It is a further object of the invention to provide a hydraulic coupling comprising a reciprocable plunger for controlling the discharge of working fluid from the coupling members, inv

which the centrifugal force exerted upon the controlling plunger is, at least in part, hydraulically balanced.

A still further object of the invention consists in the provision or a hydraulic coupling having a reciprocable plunger for controlling the discharge of working fluid from the coupling members, in which working fluid is continuously passed by the controlling plunger during operation of the coupling.

It is still another object of the invention to provide a hydraulic coupling as set forth in the preceding paragraph, in which means is provided for allowing variation of the quantity of fluid passed by the controlling plunger during operation of the coupling.

These and other objects and advantages of the invention will appear more clearly from the following specification in connection with the accompanying drawings, in which:

Figure l is a central vertical section, in axial 2 plane, through a hydraulic coupling accordin to the present invention.

Figure 2 shows the upper portion of Figure 1 on an enlarged scale and is a section along the line 2-2 of Figure 3.

Figure 3 is a section along the line 3-3 of Figure 2.

Figure 4 is a section similar to Figure 3, however with the controlling plunger in closed position.

Figure 5 is a section similar to Figure 3, show ing a slight modification with regard to the latter.

Figure 6 is a view similar to Figure 2, however showing an oval shaped discharge opening.

Figure '7 is a section along the line 1-1 oi. Figure 6.

Figure 8 we '7.

Figure 9 is a view of Figure 7, rection of the arrows 9-'9.

Figure 10 is an end view of the coupling casing showing the arrangement of the discharge bores.

Figure 11 shows a further embodiment of the invention, and

Figure 12 is a. section along the line l2l2 of Figure 11.

Figure 13 is a section similar toFigure 11 and illustrates a still further embodiment of the invention.

Figure 14 is a section ing a slight modification, and

Figure-15 is a partial section taken at right is a section along the line 8-8 of Fig seen in the diangles to Figure 14 and through the ring valve thereof.

General arrangement The hydraulic coupling according to the present invention comprises driving and driven shafts with primary and secondary rotors and a casing attached to one of the rotors. The casing is provided with one or more discharge ports having transversely arranged valve bores'adjacent these ports. A piston valve member is arranged to be reciprocable in each valve bore to cover and uncover the discharge ports and is continuously urged by spring means in one direction, whereas a fluid source is adapted selectively to move said valve member in the other direction against the thrust of the spring. The primary feature of the present invention consists in that a continuous stream of driving fluid is passing by the controlling plunger for controlling the discharge of working fluid from the coupling members so that any impurities in the driving fluid, when subjected to similar to Figure 5, showcentrifugal force. will be enabled to pass by said controlling plunger thereby preventing the accumulation of such impurities between vital movable parts of the discharge control valve.

In the principal form of the invention the discharge controlvalve is normally closed with the plunger over the discharge port. In this form the valve is opened by the pressure fluid. such as compressed air or liquid under pressure, reaching its valve operating chamber from the independent source which is separate from the source of supply of the working liquid.

According to a further embodiment of the invention, working fluid is conveyed to the controlling plunger of the discharge valve so as to exert a pressure on the plunger which, at least in part, balances the centrifugal force exerted on said plunger.

Structural arrangement Referring to the drawings in detail, Figure 1 shows the hydraulic coupling according to the present invention, which comprises driving and driven shafts i9 and II having'secured thereto a primary rotor or impeller i2, and a secondary rotor or runner II, for instanc by means of bolts i4. Bolted to the secondary rotor N ha housing It having a peripheral portion IS. The primary and secondary rotors l2 and I! are provided with blades or vanes II and I9 and core rings i9 and 29, respectively, operating in a working chamber 2|. The peripheral casing portion I9 is provided with discharge ports 22 and 23 traversed by a transverse bore 24 having a sleeve 29 mounted therein. Reciprocably mounted in the bore 24 of the sleeve '29 is a controlling plunger, generally designated 21, with two spaced piston heads 29 and 29 interconnected by a piston rod 29. The controlling plunger is preferably made hollow and or light material so as to reduce the inertia of the plunger to a minimum. The piston head 29 engages, in its outermost right hand position, the

sleeve portion II 'of a closure member 92 con nected with the sleeve in any convenient man- 'ner. Passing through the closure member 32 and vslidably mounted therein is a tubular support 99 with a head 94 connected thereto, which head is adapted to engage the flangedportion 99 of the controlling plunger 21 and is engaged y one end of a spring 39, the other end of which engages the wall 91 of the closure member 22. The tubular support It prevents the coil spring 99 from being thrown out of line at its mid-portion and from interfering with the valve movement which may be caused by the centrifugal force developed when the housing I! is in rotation.

The sleeve 29 is provided adjacent the port 22 with openings 99 and 99 which, according to the 1 embodiments of Figures 2 to 5, are circular. As

willbeseenfromFigure3,theopening lthasits rim portions beveled so that the fluid passing through the port 22 can easily pass the opening 29 to be discharged therethroiigh. As will fur- .thermore be seen from Figure 3. the opening 99 is so arranged that no accumulation or whirl of fluidcan occur at the entrance of said opening.

The port 22 communicates with a bore 49 passing through the peripheral portion i9 and having .a threaded upper portion 4| engaged by a correspondingly threaded plug 42. According to Figures2to4,thepiug42 hasaninnerthread 49 engaged by a correspondingly threaded plug 44 with an opening 49 therein.

According to the embodiment of Figure 5, the plug 420 has a constant discharge opening 490 in contrast to the embodiment in Figure 3. in which, by removing the plug 44 and replacing the same by another plug, the discharge opening may be varied without exchanging the plug 42. The discharge openings 49 and 490 communicate with an exhaust for instance, with a collector surrounding the coupling. As will be seen from Figures 2 and 3, communication is efl ected between the interior of the coupling members i2 and I2 and the discharge port 29 when the controlling plunger 21 has reached its outermost right-hand position, in which the piston head 29 engages the sleeve portion 9! of the closure member 22. When the piston head 29 is in its outermost left-hand position in which it engages the pin 46 passing through the sleeve 29, the pistcm head 29 closes the opening 29, while a limited quantity of working fluid continuously passes through the port 22 by the controlling plunger 21 and discharges through the restricted discharge openin 45. In this way any impurities in the working fluid which will be thrown to the periphery of the coupling members due to the centrifugal force developed during the operation of the coupling may escape through one or more of the restricted discharge openings 45, 45a, thereby preventing accumulation of such impurities between the piston head 29 and the sleeve 29, as was sometimes the case with previous similar constructions, in which the piston head 29 controlled the port 22. Preferably a plurality of valve arrangements, as shown in Figure 2, are provided along the periphery of the coupling housing ii, as is illustrated in Figure 10. As will be seen from Figures 3 to 5 and 7, the edges of opening 39 protrude somewhat beyond the adjacent casing wall portions. This is advantageous inasmuch as it prevents any dirt pocket between the sleeve 25 and the plunger 21.

The bore 29 of each sleeve 25 opens into an annular channel 41 in the flange 49 of the secondary rotor ii. The channel 4! completely encircles the coupling and is connected by the passageways 49 to bores 99. Each of the bores 59 is closed at one end by a threaded plug 9} and has secured in the other end thereof an axially directed conduit 52. The plug ll comprises a leak port 53 through which fluid may escape into a collecting container and has at its inner surface a dirt collecting pocket bid.

The conduit 92 passes through the core ring 29 and secondary rotor fln 54 and terminates in a bore 55 leading to an annularchamber 96 within a ring-shaped member 51 connected by bolts 99 to the flanged portion 59 of the secondary rotor l3. It will be understood that the ring-shaped member 51 comprises a plurality of such bores pling, which working fluid is supplied to the coupling'through the shaft bore 93.

The embodiments shown in Figures 6 to 9 are somewhat similar to the embodiments of Figures 2 to 5 and differ therefrom primarily in the shape 1 of the discharge openings 39 and 99.

According to the embodiment of Figure 11, the peripheral portion it of the coupling is provided with a discharge passageway 494: which is so constructed that the fluid passing therethrcugh has to change its direction before it reaches the restricted discharge opening 45. In this way fluid will accumulate in the portion 64 o! the discharge passageway 40a due to the cenfrom the pocket 65 by unthreading the plugs 44 and 42.

Finally, with regard to Figure 13, the embodiment shown therein is similar to the embodiment of Figure 11 but differs therefrom in that the plug 44 with the restricted discharge opening 45 and the plug 42 are replaced by a single plug 66, the lower surface of which is provided with a large dirt collecting pocket 61. Also in this embodiment a portion of the working fluid will, due to the centrifugal force acting thereupon, cause it to pass through the passageway 4011 so that the dirt particles will slide along the surface 68 and be collected in the pocket 61, while pressure will develop in the portion 64b of the passageway 40b and act upon the controlling plunger 21, 35, so as at least in part to counteract the centrliugalforce imparted upon the controlling plunger 21, 35, due to the rotation or the housing 15. The plug 86 may from time to time be removed from the housing IE to discharge the dirt collected in the pocket 61.

Operation In the operation of the construction shown in the drawings, the driving shaft Hi and primary rotor l2 are started in rotation by the starting of the engine, or other prime mover,to which the driving shaft i0 is connected. Working fluid 13 then supplied from the fillin Pump (not shown) through the driven shaft bore 63 to the working chamber 2i. The plunger valve member 21 is in its normally closed position, shutting off communication between the discharge port 22 and the discharge opening 23. Consequently, the coupling is filled with working fluid so that rotation of the primary rotor I2 is then conveyed to the secondary rotor i3 by the interaction of their blades l1 and 18 upon the working fluid. While the coupling is in operation, a limited quantity of fluid will continuously pass through the discharge port fluid passes from the pipe 82, through the cross pipe 6|, into the annular chamber 56 oil the ringshaped member 51, thence outwardly through the conduits 52, the bores 50 and the passageways 49 into the annular channel 41 from where it flows to the bore- 28 of the sleeve 25 to act against the end or the valve plunger 21. The thus exerted pressure torces the valve plunger 21 toward the right, against the thrust of the coil spring 44. thereby releasing the discharge openings II and 29 and establishing communication between the discharge ports 22 and 22. Due to the influence of centrifugal force, the working liquid is rapidly discharged through the discharge ports 22 and 22, and the secondary rotor ll halts after the working chamber 21 becomes empty.

To refill the coupling the operator again shifts the control valve, cutting oi! the supply or pressure fluid to the pipe 82, and connecting the annular channel 41 with an exhaust, thereby releasing the control pressure acting upon the controlling plunger 21. Under the influence oi the coil springs 26, each valve plunger 21 then returns to its normally closed position with the valve head 29 closed over the discharge openings 38 and 39.v The coupling may now be filled in the manner previously described. Refilling of the couplings is not aflected by the continuously open limited discharge openings 45 and 45a since these openings allow only a rather limited discharge and are intended merely for maintaining a continuous flow adjacent the controllin plunger 21 so as to prevent any accumulation of impurities between vital movable portions of the controlling valve plunger and the cylinder portions of the sleeve 25 engaged thereby. However, if desired, any convenient closure means, as for instance a sliding ring with slots therein, may be provided around the restricted openings 45, 45a, which may be shifted so as temporarily to close the restricted discharge openings at the refilling period of the couplings while, when the couplings are filled, the

ring is shifted so that the slots therein are in alignment with the restricted openings 45, 45a.

It will be understood that Idesire to comprehend within my invention such modifications as come within the scope of the claims.

Having thus fully described my invention, what I claim as new and desire to secure by Letters Patent is:

1. In a hydraulic coupling, a primary rotor, a secondary rotor, said primary rotor being adapted to be connected with a prime mover, means, for supplying working fluid to said rotors, a casing surrounding said rotors and having a. radially arranged discharge channel therein, a discharge opening in said casing, a reciprocable valve member with spaced piston heads adapted selectively to eflect communication between said discharge channel and said discharge opening, means for continuously passing working fluid past said valve member from the inlet portion 0! the discharge channel, means for holding said valve member closed during operation of said coupling, and means for opening saidvalve member to effect communication between said radial channel and said discharge opening.

2. In a hydraulic couplin a primary rotor, a secondary rotor, said primary rotor being adapted to be connected with a prime mover, means for supplying working fluid to said rotors, a casing enclosing said rotors and having a radially arranged discharge passageway therein with a restricted discharge opening adjacent the periphery of said casing, a valve bore substantially at right angles to said discharge passageway and adapted directly to communicate with the latter, said passageway being laterally offset with respect to said valve bore for causing particles in said working fluid and heavier than the latter to pass by said valve bore and to said discharge opening,'a discharge port in said casing for a fast-discharge or working fluid from said rotors, and a "dumping trolling communication between said discharge passageway and said discharge port, and choke means continuously connecting the radially outermost portion of said discharge passageway with an exhaust.

4. In a hydraulic coupling, a primary rotor, a secondary rotor,- means for supplying working fluid to said rotors, a casing enclosin said rotors and having a discharge passageway radially arranged therein and in continuous communication with the interior of said rotors, a valve bore having a first opening therein continuously communicating with said passageway, and a second opening arranged in alignment with said first opening and communicating with an exhaust, the rim portions of said flrst opening being beveled, said valve bore being transverse to said discharge passageway but axially oflset with regard thereto, a plunger reciprocably mounted in said valve bore for controlling communication between said sec-' and opening and said passageway, a restricted fluid outlet continuously communicating with said discharge passageway for continuously discharging a restricted quantity of working fluid from said rotors, and conduit means for selectively conveying pressure fluid to said plunger to actuate the same.

5. In a hydraulic coupling, Primary and secondary rotors, means for supplying working fluid to said rotors, a casing associated with said rotors, a dumping valve in said casing adapted, in open position, to effect a fast discharge of working fluid from said rotors, conduit means provided in said casing and continuously hydraulically connecting said rotors with said dumping valve, and a member connected to said casing and detachable therefrom independent of said dumping valve for allowing a limited quantity of fluid to escape from said rotors while the latter are being rotated, said member being oflset with regard to said dumping valve and being provided with a chamber communicating with said conduit means at a point located between said rotors and said valve at a distance from the axis of rotation of said rotors greater than the distance between said valve and said axis, whereby foreign material in said working fluid is collected in said chamber before said working fluid reaches said dumping valve.

6. In a hydraulic coupling, a primary rotor, a secondary rotor, means for supplying working fluid to said rotors, a casing surrounding said rotors and including a restricted normally open passageway for conveying working fluid to an exhaust, a sleeve extending into said passageway and having an opening with its rim portions protruding beyond .adjacent wall portions of said passageway, an exhaust port in said sleeve, and a dumping piston slidably mounted in said sleeve and operable selectively to open or close said opening.

7. In a hydraulic coupling, a primary rotor, a secondary rotor. said primary rotor being adapted to be connected with a prime mover, means for supplying working fluid to said rotors, a :casing connected to one of said rotors and having a.

discharge passageway therein, a valve bore substantially at right angles to said discharge passageway having the axis thereof offset with respect to the axis of said discharge passageway, a discharge port in said casing communicating with an exhaust, conduit means adapted to connect said valve bore with said discharge passageway, and having its axis passing substantially through the axis of said valve bore, said conduit means communicating with a continuously open restricted discharge aperture for allowing a continuous but limited escape of working fluid from said rotors, and valve means reciprocably mounted in said valve bore for selectively eflecting or interrupting communication between said conduit means and said discharge port, said conduit means being arranged so as to cause accumulation of driving fluid between said valve bore and said discharge aperture during the operation of said coupling for exerting pressure obtained by the action of centrifugal force on the accumulated driving fluid on said valve means to counteract the centrifugal force imparted thereon due to the rotation of said rotors.

8. In a hydraulic coupling, a primary and secondary rotor, a casing connected to one of said rotors and having a passageway therein in continuous hydraulic communication with said rotors, said passageway having a substantially radially arranged first portion, and a second portion directly communicating with said first portion but forming an angle therewith, restricted discharge means directly communicating with said second portion for allowing continuous escape of a restricted quantity of fluid from said rotors during operation thereof, and a reciprocable valve member in continuous hydraulic communication with said second passageway portion and spaced from the axis of rotation of said rotors by a distance less than the distance between said axis and said restricted discharge means, thereby causing the fluid conveyed by centrifugal force from said rotors to said restricted discharge means and throttled by the latter to counteract at least in part the centrifugal force-imparted upon said valve member during operation of said rotors, said valve member being movable selectively into position for establishing fluid connection between said passageway and an outlet opening to enable a fast decrease in the quantity of fluid in said rotors.

9. In a hydraulic coupling comprising a primary rotor, a secondary rotor and means for supplying working fluid to said rotors, the combina-. tion therewith of means forming a valve casing carried by said secondary rotor and having a discharge port therein, a piston type dumping valve in said casing for controlling opening of said discharge port having a line of 'movement that is angular to the action of centrifugal force acting upon the same during rotation of said rotors, means for actuating said valve, and a discharge passage continuously hydraulically connecting the working fluid within said rotors with said valve. having such a longitudinal contour as to direct working fluid from within said rotors urged centrifugally outwardly by rotation of the rotors upon the surface of the piston valve only in direct opposition to the action oi centrifugal force acting upon the piston valve to at least in part counterbalance the centrifugal force on the valve to relieve frictional resistance to movement of the valve in the casing.

10. In a hydraulic coupling comprising primary and secondary rotors adapted to be filled with working fluid, the combination therewith of a dumping valve movable substantially parallel to the axis of rotation of said rotors and operable independently oi said rotors to discharge said working fluid from said rotors, and a discharge passage continuously hydraulically connecting the'working fluid within said rotors with said valve having such a longitudinal contour as to direct working fluid from within said rotors urged centrifugally outwardly by rotation of the rotors upon the surface of the valve only in direct'opposition to the action of centrifugal force acting upon the valve to at least in part counterbalance the centrifugal force on the valve to relieve frictional resistance to movement of the valve in the casing.

11. In a hydraulic coupling comprising primary and secondary rotors adapted to be filled with working fluid, the combination therewith of a dumping valve movable substantially parallel to the axis of rotation of said rotors and operable independently of said rotors to discharge said working fluid from said rotors, a discharge passage continuously hydraulically connecting the working fluid within said rotors with said valve having such a longitudinal contour as to direct working fluid from within said rotors urged centriiugally outwardly by rotation 01 the rotors upon the surface of the valve only in direct opposition to the action or centrifugal force acting upon the valve to at least in part counterbalance the centrifugal force on the valve to relieve frictional resistance to movement of the valve in the casing, and a dirt collecting pocket having a continuously open discharge opening connected thereto located in said discharge passage and positioned therein ahead of the valve means to centrifugally collect and discharge some of the foreign material from the hydraulic fluid in the coupling to prevent it from depositing or collecting on the valve.

NOAH L. ALISON.

REFERENCES CIT D The following references are of record in the file of this patent:

UNITED STATES PATENTS 

